US4756203A - Intermittent drive mechanism - Google Patents

Intermittent drive mechanism Download PDF

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Publication number
US4756203A
US4756203A US07/078,651 US7865187A US4756203A US 4756203 A US4756203 A US 4756203A US 7865187 A US7865187 A US 7865187A US 4756203 A US4756203 A US 4756203A
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United States
Prior art keywords
intermediate shaft
spline
shaft
cam
rigid circular
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/078,651
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English (en)
Inventor
Yasuhiko Matsuda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
YKK Corp
Original Assignee
Yoshida Kogyo KK
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Application filed by Yoshida Kogyo KK filed Critical Yoshida Kogyo KK
Assigned to YOSHIDA KOGYO K.K. reassignment YOSHIDA KOGYO K.K. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MATSUDA, YASUHIKO
Application granted granted Critical
Publication of US4756203A publication Critical patent/US4756203A/en
Assigned to YKK CORPORATION reassignment YKK CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: YOSHIDA KOGYO K.K.
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H27/00—Step-by-step mechanisms without freewheel members, e.g. Geneva drives
    • F16H27/04—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H49/00—Other gearings
    • F16H49/001—Wave gearings, e.g. harmonic drive transmissions
    • D—TEXTILES; PAPER
    • D05—SEWING; EMBROIDERING; TUFTING
    • D05B—SEWING
    • D05B35/00—Work-feeding or -handling elements not otherwise provided for
    • D05B35/06—Work-feeding or -handling elements not otherwise provided for for attaching bands, ribbons, strips, or tapes or for binding
    • D05B35/064—Work-feeding or -handling elements not otherwise provided for for attaching bands, ribbons, strips, or tapes or for binding for attaching slide fasteners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18528—Rotary to intermittent unidirectional motion
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19555—Varying speed ratio
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y10T74/19884—Irregular teeth and bodies

Definitions

  • the present invention relates to an intermittent drive mechanism for use in an intermittently operative apparatus, such as an apparatus for intermittently feeding a tape-like flexible elongate material by and between a cooperative pair of feed and presser rollers.
  • FIG. 10 which mechanism comprises a gear ratchet including a drive pawl 101 pivoted to one end of a lever 102 and meshing with a toothed ratchet wheel 103 fixed on a drive shaft 104, the other end of the lever 102 being slidably fitted over an eccentric cam 105 connected with a driven shaft 106.
  • the drive pawl 101 moves back and forth in the directions of the arrowheads A to thereby turn the ratchet wheel 103 and hence the driven shaft 106 stepwise in the counterclockwise direction.
  • the drive mechanism further includes a friction brake unit composed of a brake drum 107 secured to the drive shaft 106, a pair of brake shoes 108, 109 secured to confronting inner edges of a pair of brake levers 110, 111 disposed on opposite sides of the brake drum 107, and a spring 112 acting between the brake shoes 108, 109 to urge them toward each other into frictional engagement with the brake drum 107.
  • a friction brake unit composed of a brake drum 107 secured to the drive shaft 106, a pair of brake shoes 108, 109 secured to confronting inner edges of a pair of brake levers 110, 111 disposed on opposite sides of the brake drum 107, and a spring 112 acting between the brake shoes 108, 109 to urge them toward each other into frictional engagement with the brake drum 107.
  • the known intermittent drive mechanism thus constructed is disadvantageous in that it cannot precisely control the stepwise angular motion of the driven shaft 106 bacause the stopping timing of the stepwise motion is solely dependent on a friction or braking force exerted by the friction brake unit.
  • the ratchet wheel 103 is likely to overrun while it is driven at a high speed.
  • the contacting components, particularly the brake shoes 108, 109 and the drive pawl 101 are progressively worn out while in use, and hence a frequent adjustment or maintenance of such components is required.
  • Another drawback is that the components in the drive mechanism themselves and other components driven by the drive mechanism are likely to be damaged due to undue shock forces applied thereto when the stepwise movement of the driven shaft 106 is started and stopped abruptly in such a manner that the angular speed of the drive shaft varies in a rectangular pulse-like fashion, as shown in FIG. 11.
  • an intermittent drive mechanism includes a non-circular drive gear secured to an input shaft rotating at a constant speed, a non-circular driven gear fixedly mounted on an intermediate shaft and held in driven mesh with the drive gear, and a speed reducer drivingly connecting the intermediate shaft to an output shaft.
  • the speed reducer includes an elliptical cam fixedly connected with the intermediate shaft, an externally toothed flexible spline slidably fitted over the elliptical cam and firmly connected with the output shaft, and an internally toothed rigid circular spline rotatable relatively to the intermediate shaft.
  • the flexible spline has teeth less in number than teeth on the rigid circular spline and meshes with the rigid circular spline at two diametrically opposite regions extending along a major axis of the elliptical cam.
  • a crank lever operatively connects an eccentric cam on the input shaft with the rigid circular spline so as to transmit a reciprocating rotary motion to the rigid circular spline.
  • the flexible spline rotates one turn only when the elliptical cam has completed a number of turns which correspond to a value obtained by dividing the number of teeth of the rigid circular spline by the number of aforesaid teeth of difference.
  • the rigid circular spline is turned through one half of the foregoing angle in the same direction as the elleptical cam while the elleptical cam moves through a first half of a single turn, the flexible spline will remain immovable or non-rotatable relatively to the elliptical cam.
  • the foregoing reciprocating angular movement of the rigid circular spline is controlled by the eccentric cam.
  • the eccentric cam is connected with the rigid circular spline via the crank lever such that for each turn of the intermediate shaft, one-half of the reduced, non-uniform velocity rotary motion of a sinusoidal pattern is transmitted from the intermediate shaft to the output shaft to turn the latter, whereas the rest of the rotary motion of the intermediate shaft is not transmitted to the output shaft. Consequently, the output shaft turns stepwise in one direction.
  • the stepwise movement of the output shaft takes place gently without causing undesired shock because both of the pair of non-circular drive and driven gears and the pair of flexible and rigid splines are continuously meshing with each other.
  • the starting and stopping timing of the intermittent rotary motion can accurately be controlled.
  • the gear trains are relatively unsusceptible to abrasive wear and hence easy to maintain.
  • FIG. 1 is a fragmentary perspective view of an intermittent drive mechanism embodying the present invention
  • FIG. 2 is a schematic plan view of the mechanism shown in FIG. 1;
  • FIG. 3 is a cross-sectional view taken along line III--III of FIG. 2, showing non-circular drive and driven gears of the mechanism;
  • FIG. 4 is an enlarged longitudinal cross-sectional view of a speed reducer of the mechanism
  • FIG. 5 is an enlarged cross-sectional view taken along line V--V of FIG. 4;
  • FIG. 6 is a cross-sectional view taken along line VI--VI of FIG. 2, showing a connection between an eccentric cam and an annular bracket of the mechanism;
  • FIG. 7 is a graph showing a pattern of the angular speed of an intermediate shaft obtained by the non-circular drive and driven gears of the mechanism
  • FIG. 8 is a graph illustrative of the speed reduction property of the speed reducer shown in FIGS. 4 and 5;
  • FIG. 9 is a graph showing a pattern of the angular speed of an output shaft of the mechanism shown in FIG. 1;
  • FIG. 10 is a schematic plan view of a prior intermittent drive mechanism.
  • FIG. 11 is a graph showing a pattern of the intermittent motion produced by the mechanism of FIG. 10.
  • an intermittent drive mechanism embodying the present invention is particularly useful when incorporated in a sewing unit in a slide fastener manufacturing apparatus.
  • a frame, bearing members and a drive motor of the intermittent drive mechanism are omitted for clarity.
  • the intermittent drive mechanism comprises an input shaft 12 driven by the drive motor to rotate at a constant velocity and supporting thereon a non-circular drive gear 13 for corotation therewith.
  • the drive gear 13 is held in driving mesh with a non-circular driven gear 14 fixedly connected with an intermediate shaft 15 extending parallel to the input shaft 12.
  • the non-circular drive and driven gears 13, 14 have an elliptical shape and they serve to translate a constant velocity rotary motion of the input shaft 12 into a non-uniform velocity rotary motion of the intermediate shaft 15.
  • the rotary motion of the intermediate shaft 15 has an angular velocity varying in a sinusoidal pattern, as shown in FIG. 7.
  • the intermediate shaft 15 is operatively connected with an output shaft 16 through a speed reducer 17.
  • the output shaft 16 carries thereon a toothed drive pulley 18 connected by a synchronous belt 19 with a toothed driven pulley 20.
  • the driven pulley 20 is fixedly mounted on a drive shaft 21 of a feed unit 22.
  • the feed unit 22 includes a feed roller 23 secured to the drive shaft 21, and a presser roller 24 associated with the feed roller 23 for urging a continuous slide fastener chain 25 against the feed roller 23.
  • the feed unit 22 is driven by the present intermittent drive mechanism to feed the slide fastener chain 25 stepwise in a longitudinal direction, in synchronism with the operation of a sewing machine 26.
  • the speed reducer 17 includes an elliptical cam 27, an externally toothed flexible spline 28 slidably mounted around the elliptical cam 27 via a ball bearing 29, and an internally toothed rigid circular spline 30 held in mesh with the flexible spline 28 at two diametrically opposite regions extending along a major axis of the elliptical cam 27.
  • the flexible spline 28 is formed of a toothed steel belt and has external teeth at least two less in number than the internal teeth on the rigid circular spline 30.
  • the flexible spline 28 has 46 external teeth while the rigid circular spline 30 has 52 internal teeth.
  • the elliptical cam 27 is fixedly mounted on the input shaft 15 for corotation therewith.
  • the flexible spline 28 is fixedly connected with the output shaft 16 (FIG. 4) while the rigid circular spline 30 is secured to a hollow cylindrical casing 31 rotatably mounted on the intermediate shaft 15 and the output shaft 16 by means of sets of ball bearings, not designated.
  • the input shaft 12 has fixed thereon an eccentric cam 32 on which a crank lever 33 is mounted via a roller bearing 34.
  • the free end of the crank lever 33 is pivotably connected by a pin 35 with an arm 36 projecting radially outwardly from an annular bracket 37 concentrically secured to the casing 31 by a plurality of screws 38.
  • the eccentric cam 32 has a cam profile designed such that when the input shaft 12 and hence the cam 32 rotates one turn, the casing 31 and therefore the rigid circular spline 30 angularly moves back and forth through an angle ⁇ 1 which is half the angle defined jointly by the number of teeth of difference between the rigid circular spline 30 and the flexible spline 28.
  • one of the teeth 38 on the flexible spline 28, which is meshing with one tooth 39 on the rigid circular spline 30, will mesh with a sixth succeeding tooth 40 on the rigid circular spline 30 when the elliptical cam 27 has rotated one turn.
  • the rigid circular spline 30 is reciprocated through the angle ⁇ 1 which is three times as large as the tooth pitch of the rigid circular spline 30, as shown in FIG. 5.
  • the angular reciprocating movement of the rigid circular spline 30 is linked with the rotary motion of the intermediate shaft 15 in the manner as described below.
  • the rigid circular spline 30 is turned through the angle ⁇ 1 in the same direction (clockwise in FIG. 5) as the intermediate shaft 15 with the result that the flexible spline 28 remains immovable or non-rotatable relatively to the elliptical cam 27 and hence the intermediate shaft 15.
  • the tooth 31 on the flexible spline 28 is brought into meshing engagement with a tooth 41 on the rigid circular spline 30.
  • the rigid circular spline 30 is turned in the opposite direction (counterclockwise in FIG. 5) through the same angle ⁇ 1 . Consequently, the tooth 31 on the flexible spline 28 turns counterclockwise through an angle ⁇ 2 , into meshing engagement with the tooth 40 on the rigid circular spline 30.
  • the flexible spline 28 has turned counterclockwise through an angle equal to the sum of ⁇ 1 and ⁇ 2 , relatively to the intermediate shaft 15 as the latter has rotated one turn.
  • FIG. 8 shows a deceleration or speed-reduction property of the speed reducer 17.
  • the flexible spline 28 remains immovable relatively to the intermediate shaft 15 as the latter turns through a first half of one turn, while it is active to effect speed reduction only when the intermediate shaft 15 is turning through the next succeeding half-turn.
  • Due to rigid connection with the flexible spline 28, the output shaft 16 is also immovable during the first half-turn of the intermediate shaft 15 and is rotated during the second half-turn of the intermediate shaft 15.
  • the flexible and rigid splines 28, 30 continuously mesh with each other with the result that the rotary motion can be transmitted gently without causing abrupt fluctuation in angular speed at the beginning and the end of the motion.
  • the motion of the decelerated angular speed pattern shown in FIG. 8 is combined with the motion of the sinusoidal angular speed pattern shown in FIG. 7 when the rotary motion of the intermediate shaft 15 is transmitted to the output shaft 16 through the speed reducer 16. With this combination, the output shaft 16 is rotated stepwise in a pattern as shown in FIG. 9. The rotary motion of the output shaft 16 thus obtained takes place gently without causing abrupt fluctuation in angular speed.
  • the eccentric cam 32 has a cam profile designed such that the intermittent motion is transmitted to the output shaft 16 when the angular speed of the intermediate shaft 15 becomes maximum. It is possible to modify the cam profile or the relative angular position of the cam 32 and the input shaft 12 to thereby vary the timing of the intermittent rotary motion of the output shaft 16.
  • the intermittent drive mechanism of the present invention includes a cooperative pair of non-circular drive and driven gears, and a speed reducer having an internally toothed rigid circular spline and an externally toothed flexible spline meshing with the rigid spline.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)
US07/078,651 1986-07-28 1987-07-28 Intermittent drive mechanism Expired - Fee Related US4756203A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP61176895A JPS6334344A (ja) 1986-07-28 1986-07-28 間欠駆動装置
JP61-176895 1986-07-28

Publications (1)

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US4756203A true US4756203A (en) 1988-07-12

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US07/078,651 Expired - Fee Related US4756203A (en) 1986-07-28 1987-07-28 Intermittent drive mechanism

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US (1) US4756203A (enrdf_load_stackoverflow)
EP (1) EP0254958B1 (enrdf_load_stackoverflow)
JP (1) JPS6334344A (enrdf_load_stackoverflow)
KR (1) KR900007364B1 (enrdf_load_stackoverflow)
BR (1) BR8704154A (enrdf_load_stackoverflow)
CA (1) CA1272045A (enrdf_load_stackoverflow)
DE (1) DE3763231D1 (enrdf_load_stackoverflow)
ES (1) ES2015012B3 (enrdf_load_stackoverflow)
HK (1) HK64093A (enrdf_load_stackoverflow)
MY (1) MY101258A (enrdf_load_stackoverflow)
SG (1) SG39293G (enrdf_load_stackoverflow)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4874067A (en) * 1986-11-07 1989-10-17 R. A. & Co. Inc. Jones Automatic changeover for cartoners
US5111707A (en) * 1990-04-11 1992-05-12 Mitsubishi Denki K.K. Engine starter apparatus
US5343645A (en) * 1992-02-20 1994-09-06 Quality Manufacturing Incorporated Multi-faceted display drive mechanism
US6269711B1 (en) * 1998-08-12 2001-08-07 Teijin Seiki Company Limited Transmission device using flexible gear
US20040154434A1 (en) * 2003-02-05 2004-08-12 Peter Murin Geared segments with variable gear ratio
US6817267B2 (en) * 2001-02-19 2004-11-16 Harmonic Drive Systems Inc. Actuator having a wave gear reduction drive
WO2005026583A1 (en) * 2003-09-18 2005-03-24 Litens Automotive Partnership Non-circular rotary component
US20050262984A1 (en) * 2004-04-15 2005-12-01 Hetcher Jason D Miter adjustment assembly for a saw
CN100357633C (zh) * 2003-12-29 2007-12-26 石永刚 摆线滚子链谐波减速器
US20110239874A1 (en) * 2010-04-01 2011-10-06 Columbia Insurance Company Drive system
CN102387896A (zh) * 2009-05-20 2012-03-21 利优比株式会社 冲击工具
US20120264556A1 (en) * 2011-04-12 2012-10-18 William Terry Lester Translating Gear Set with Linkages
USD706604S1 (en) * 2013-08-15 2014-06-10 Bing-Sheng Chen Clamping member of loading and unloading device suitable for various pipes
DE102015201589A1 (de) * 2015-01-29 2016-08-04 Volkswagen Aktiengesellschaft Mehrstufiger Steuertrieb zwischen einer Kurbelwelle und mindestens einer Nockenwelle eines Verbrennungsmotors
US20160281827A1 (en) * 2014-09-09 2016-09-29 Solystic A Mechanical Transmission For a Mail Stacker Unit With a Clutch Brake and Elliptical Gearing
USD798059S1 (en) * 2014-12-29 2017-09-26 Church & Dwight Co., Inc. Bristle support plate for toothbrush
US11199040B2 (en) * 2017-09-25 2021-12-14 Nidec Sankyo Corporation Rotation transmission mechanism and damper device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9211772U1 (de) * 1992-09-02 1994-01-13 Horst Witte Entwicklungs- und Vertriebs-KG, 21369 Nahrendorf Zusatzgerät für Werkzeugmaschinen
DE19601300C2 (de) * 1996-01-16 2003-04-17 Ver Deutscher Werkzeugmaschine Antriebseinrichtung für eine Umformmaschine
IT1299849B1 (it) * 1998-02-18 2000-04-04 Gd Spa Unita' per il trasferimento di prodotti.
DE502006006469D1 (de) * 2006-11-24 2010-04-29 Groz Beckert Kg Getriebe für einen Webschaftantrieb
DE102009002132A1 (de) * 2009-04-02 2010-10-07 Robert Bosch Gmbh Hochdruckpumpe
CN105220373B (zh) * 2014-06-25 2019-06-28 飞马缝纫机制造株式会社 送出臂型缝纫机
JP6320235B2 (ja) * 2014-08-07 2018-05-09 ヤンマー株式会社 田植機
US9809912B2 (en) * 2014-10-16 2017-11-07 Handi Quilter, Inc. Vibration reduction mechanism for a sewing machine
US8997669B1 (en) 2014-10-16 2015-04-07 Handi Quilter, Inc. Thread tensioner for a sewing machine
US9394639B2 (en) 2014-10-16 2016-07-19 Handi Quilter, Inc. Motorized thread tensioner for a sewing machine
CN112359504A (zh) * 2020-10-10 2021-02-12 安徽尚豪齿轮科技有限公司 一种缝纫机下送料机构
CN112871931A (zh) * 2021-01-05 2021-06-01 邱波 一种检验科用试管清洗装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1449845A (en) * 1921-08-09 1923-03-27 John F Mayer Rotatable container machine
US2700285A (en) * 1955-01-25 Bellini
US2861635A (en) * 1955-01-27 1958-11-25 United States Steel Corp Power transmitting apparatus
US3424021A (en) * 1967-05-23 1969-01-28 Ferdinand Freudenstein Intermittent motion mechanism employing non-circular gears
US3435790A (en) * 1967-05-12 1969-04-01 Union Special Machine Co Intermittent output transmission
US3613470A (en) * 1968-09-07 1971-10-19 Tsudakoma Ind Co Ltd Gear transmission mechanism of a weaving loom
US4012964A (en) * 1975-02-14 1977-03-22 Yuan Ho Lee Intermittent rotary mechanism

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2700285A (en) * 1955-01-25 Bellini
US1449845A (en) * 1921-08-09 1923-03-27 John F Mayer Rotatable container machine
US2861635A (en) * 1955-01-27 1958-11-25 United States Steel Corp Power transmitting apparatus
US3435790A (en) * 1967-05-12 1969-04-01 Union Special Machine Co Intermittent output transmission
US3424021A (en) * 1967-05-23 1969-01-28 Ferdinand Freudenstein Intermittent motion mechanism employing non-circular gears
US3613470A (en) * 1968-09-07 1971-10-19 Tsudakoma Ind Co Ltd Gear transmission mechanism of a weaving loom
US4012964A (en) * 1975-02-14 1977-03-22 Yuan Ho Lee Intermittent rotary mechanism

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4874067A (en) * 1986-11-07 1989-10-17 R. A. & Co. Inc. Jones Automatic changeover for cartoners
US5111707A (en) * 1990-04-11 1992-05-12 Mitsubishi Denki K.K. Engine starter apparatus
US5343645A (en) * 1992-02-20 1994-09-06 Quality Manufacturing Incorporated Multi-faceted display drive mechanism
US6269711B1 (en) * 1998-08-12 2001-08-07 Teijin Seiki Company Limited Transmission device using flexible gear
US6817267B2 (en) * 2001-02-19 2004-11-16 Harmonic Drive Systems Inc. Actuator having a wave gear reduction drive
US7185558B2 (en) * 2003-02-05 2007-03-06 Peter Murin Geared segments with variable gear ratio
US20040154434A1 (en) * 2003-02-05 2004-08-12 Peter Murin Geared segments with variable gear ratio
US20070066430A1 (en) * 2003-09-18 2007-03-22 Witold Gajewski Non-circular rotary component
US8042507B2 (en) 2003-09-18 2011-10-25 Litens Automotive Partnership Non-circular rotary component
WO2005026583A1 (en) * 2003-09-18 2005-03-24 Litens Automotive Partnership Non-circular rotary component
CN100564950C (zh) * 2003-09-18 2009-12-02 利滕斯汽车合伙公司 非圆形旋转部件
US20090149287A1 (en) * 2003-09-18 2009-06-11 Witold Gajewski Non-circular rotary component
US7493880B2 (en) 2003-09-18 2009-02-24 Litens Automotive Partnership Non-circular rotary component
CN100357633C (zh) * 2003-12-29 2007-12-26 石永刚 摆线滚子链谐波减速器
US7798041B2 (en) 2004-04-15 2010-09-21 Milwaukee Electric Tool Corporation Miter adjustment assembly for a saw
US20050262984A1 (en) * 2004-04-15 2005-12-01 Hetcher Jason D Miter adjustment assembly for a saw
US20060162523A1 (en) * 2004-04-15 2006-07-27 Milwaukee Electric Tool Corporation Miter adjustment assembly for a saw
CN103753469A (zh) * 2009-05-20 2014-04-30 利优比株式会社 冲击工具
CN102387896A (zh) * 2009-05-20 2012-03-21 利优比株式会社 冲击工具
CN103753469B (zh) * 2009-05-20 2015-12-30 利优比株式会社 冲击工具
CN102387896B (zh) * 2009-05-20 2014-05-21 利优比株式会社 冲击工具
US20110239874A1 (en) * 2010-04-01 2011-10-06 Columbia Insurance Company Drive system
US8695490B2 (en) * 2010-04-01 2014-04-15 Columbia Insurance Company Drive system
US9089243B2 (en) 2010-04-01 2015-07-28 Columbia Insurance Company Drive system for household implements including food processor
US9964188B2 (en) 2010-04-01 2018-05-08 Columbia Insurance Company Drive system
US8663048B2 (en) * 2011-04-12 2014-03-04 William Terry Lester Translating gear set with linkages
US20120264556A1 (en) * 2011-04-12 2012-10-18 William Terry Lester Translating Gear Set with Linkages
USD706604S1 (en) * 2013-08-15 2014-06-10 Bing-Sheng Chen Clamping member of loading and unloading device suitable for various pipes
US20160281827A1 (en) * 2014-09-09 2016-09-29 Solystic A Mechanical Transmission For a Mail Stacker Unit With a Clutch Brake and Elliptical Gearing
USD798059S1 (en) * 2014-12-29 2017-09-26 Church & Dwight Co., Inc. Bristle support plate for toothbrush
DE102015201589A1 (de) * 2015-01-29 2016-08-04 Volkswagen Aktiengesellschaft Mehrstufiger Steuertrieb zwischen einer Kurbelwelle und mindestens einer Nockenwelle eines Verbrennungsmotors
US11199040B2 (en) * 2017-09-25 2021-12-14 Nidec Sankyo Corporation Rotation transmission mechanism and damper device

Also Published As

Publication number Publication date
KR880001950A (ko) 1988-04-28
MY101258A (en) 1991-08-17
SG39293G (en) 1993-06-11
JPH0459497B2 (enrdf_load_stackoverflow) 1992-09-22
ES2015012B3 (es) 1990-08-01
JPS6334344A (ja) 1988-02-15
HK64093A (en) 1993-07-09
DE3763231D1 (de) 1990-07-19
BR8704154A (pt) 1988-04-12
EP0254958B1 (en) 1990-06-13
EP0254958A1 (en) 1988-02-03
KR900007364B1 (ko) 1990-10-08
CA1272045A (en) 1990-07-31

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